EP1601875A1 - Eccentric screw pump - Google Patents

Eccentric screw pump

Info

Publication number
EP1601875A1
EP1601875A1 EP04719362A EP04719362A EP1601875A1 EP 1601875 A1 EP1601875 A1 EP 1601875A1 EP 04719362 A EP04719362 A EP 04719362A EP 04719362 A EP04719362 A EP 04719362A EP 1601875 A1 EP1601875 A1 EP 1601875A1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
pressure
area
head part
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04719362A
Other languages
German (de)
French (fr)
Other versions
EP1601875B1 (en
Inventor
Peter Rösner
Anke Stegner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ROESNER, PETER
Stegner Anke
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1601875A1 publication Critical patent/EP1601875A1/en
Application granted granted Critical
Publication of EP1601875B1 publication Critical patent/EP1601875B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits

Definitions

  • the invention relates to an eccentric screw pump, which has a stator and a rotor, between which the material to be conveyed is shifted from a suction-side input area to a pressure-side discharge area when the rotor is rotated in the stator, a pressure-volume area and a suction-volume area being located in the pressure-side discharge area the stator and the rotor are opposite and changing due to rotor rotation.
  • Known eccentric screw pumps of this type contain a rotor designed as a screw, which has the shape of a round thread screw with a high pitch and a large thread depth, and a stator, which has a thread-like inner structure and thus has the shape of a screw shell.
  • the thread-like inner structure of the stator from the suction side to the pressure side, forms cavities which are formed axially one after the other and in which the rotor rotates. Parts of the inner surface of the stator and parts of the outer surface of the rotor touch during the rotation of the rotor, with conveying chambers and associated sealing areas being present between the inner surface of the stator and the outer surface of the rotor, the material to be conveyed in the conveying chambers when the rotor is rotating in the cavities of the stator is shifted from the suction side to the pressure side along a conveyor line.
  • Such an eccentric screw pump is known from document EP 0 713 974, in which continuous rotation of abrasive material to be conveyed is possible by rotating the rotor in the cavities of the stator.
  • the stator is made of elastic material and bears against the rotor with a preload, which always creates a seal at the running chamber end.
  • the material to be conveyed pressed out of the discharge cavity on the pressure side, due to the material to be conveyed in the downstream pressure pipe, presses on the rearward conveyed material as opposing external pressure.
  • the conveying process thus builds up internal pressure, particularly against the sealing areas. The higher the external pressure built up in the pressure pipe, the greater the preload between the rotor and the stator in order to ensure a secure seal.
  • the rotor and the stator are subject to wear, particularly during the conveying of the conveyed material. Essentially, the wear occurs at the aisles of the stator designed as seals of the cavities, starting from the side of the discharge-side discharge area in the direction of the inlet-side entry area. The increase in wear causes the decrease in the delivery rate of the eccentric screw pump.
  • the elastic stator rests on the rotor with a pre-tension, whereby the material being conveyed can cause high wear between the stator and the rotor, which increases with increasing pressure. The wear progressively moves from the pressure to the suction side and removes the original sealing areas. If the internal pressure can no longer overcome the external pressure, the conveying process is finally stopped.
  • the clamping devices can be used to make radial compressions of the stator in detail or, as required, as a whole, and thus to bring the inner surface of the stator closer to the outer surface of the rotor, whereby the approximation should lead to the creation of the original seal in the sealing areas.
  • An eccentric screw pump is also known from the document DE 202 15 849.7, in which a check valve device which allows the material to be conveyed is present on the discharge-side discharge area and which includes a closure disk rigidly attached to the end face of the stator.
  • the end face of the rotor rotates on the sealing disc, which is intended to seal the changing pressure and suction volume ranges.
  • the stator-attached sealing disc has two stationary through openings for the discharge of the conveyed material, each of which is assigned a check valve.
  • the two valve-fitted through openings are assigned to the pressure volume area and suction volume area occupied by the discharge area of the rotor and are opened when the internal pressure in the respective volume areas between the stator and the rotor is greater than is the pressure pipe passing on the valve in the conveyed material.
  • stator-fastened closure disk with the valves requires additional components.
  • the valves must at least be cleaned after the eccentric screw pump has been used.
  • the invention is based on the object of specifying an eccentric screw pump which is designed in the area of the discharge in a manner which is simple to install and improves maintenance.
  • the wear in the sealing areas of the stator and rotor, in particular in the pressure area of the discharge cavity on the pressure side, is to be substantially slowed down or largely reduced.
  • the already short lengths of the stator and the rotor or the conveying path should also be further shortened and the original conveying capacity should be largely retained over a longer period of time.
  • a rotor head part which closes off the discharge-side discharge area and is fastened to the end face of the rotor and rotates with the rotor and has at least one recess through the head part which is introduced into the rotor head part in this way in relation to the holding rotor end face that the recess, which rotates in the conveying direction in conformity with the rotor, opens the pressure volume area and that a recess-free rotor head part area keeps the opposite suction volume area sealed in the opening period of the pressure volume area.
  • the rotor head part is attached to the rotor end face by screwing, welding or the like. brought about with the back of the rotor head part.
  • the rotor head part can be attached to the rotor end face in such a way that the central axis of the rotor head part can coincide with the center of the rotor end face. Then the movement of the center axis represents a centric straight-line elongation; if there is no match, an eccentric cam track can be run.
  • the continuous recess is made directly laterally on the end face of the rotor in the rotor head part, the recess cross section being specified in accordance with the dimensions with the pressure build-up within the pressure volume range and the discharge of the conveyed material by the rotating rotor.
  • the rotor head part can preferably be a perforated rotor disk with circular surfaces.
  • the associated continuous recess can preferably be an elongated hole which is largely bean-shaped in plan cross section.
  • the rotor head part is attached to the rotor end face in such a way that the hole, starting from the edge of the holding rotor end face in the radial direction with its effective opening cross section, enters the pressure volume area with the hole beginning area and later with the pressure generation within the pressure volume area with the hole beginning area Hole end area emerges from the pressure volume area again.
  • the continuous recess of the rotor head part can optionally also be designed as a radially directed sector-section-shaped through opening or sector-like recess starting from the edge of the holding rotor end face, which, like in the case of the elongated hole design with its respectively effective opening cross section, conforms to the rotor with the generation of pressure within the pressure volume range by the rotor the pressure volume area enters and exits the pressure volume area after the pressure volume area has been crossed.
  • the rotor head part has such circumferential dimensions that the rotor head part with its remaining, recess-free rotor head part area keeps the suction volume area in the area of the stator opening that is created during rotation closed.
  • the rotor can be designed as a worm in the form of a round-thread screw with a high pitch and large thread depth, the stator representing a worm shell and cavities formed axially one after the other - at least one suction-side entry cavity and one pressure-side discharge cavity - containing a conveying path, with the stator inner surface and the rotor outer surface form conveying chambers by sealing areas adapted between the stator and the rotor, the material to be conveyed in the conveying chambers being displaceable from the suction-side input area to the pressure-side discharge area when the rotor is rotated in the cavities of the stator.
  • a pressure pipe can be connected to the stator face, via which the material to be conveyed is passed, the pressure pipe can be locked on the stator in a sealed manner by means of at least one holding element that surrounds the stator and pressure pipe.
  • the invention makes it possible for the presence of the rotor head part or the rotor perforated disk on the discharge-side discharge region to separate the original pressure-tube-related pressure space after the pump outlet from the original pump-related discharge-side discharge cavity. After the discharge area on the pressure side has been opened through the opening, which is dependent on the rotor rotation, by means of the continuous recess, a subsequent gentle filling of the conveyed material is obtained from the suction-side entrance area and directed by the rotating rotor.
  • FIG. 1 shows a schematic perspective exploded view of an eccentric screw pump according to the invention with a rotor head part detached from the rotor end face and a connectable pressure pipe detached from the stator end face,
  • Fig. 2 is a schematic frontal plan view of a
  • Volume range at a fixed rotor angle ⁇ equal to 0 ' 3 shows a schematic frontal top view of the perforated rotor disk with the hole in a position with maximum discharge of conveyed material from the pressure volume range when the rotor is rotated through a rotor angle equal to 90 ° according to FIG. 2,
  • Fig. 4 is a schematic frontal top view of the perforated rotor disk with the hole in a position after the end of the discharge of conveyed material from the previous pressure volume range or at the beginning of the discharge of
  • FIG. 5 shows a longitudinal section through a shortened eccentric screw pump with the rotor perforated disk according to FIG. 3 along the line I-I.
  • FIG. 1 shows a schematic exploded view of an eccentric screw pump 1, which has a stator 2 and a rotor 3, between which the material to be conveyed is shifted from a suction-side input area 4 to a pressure-side discharge area 5 when the rotor 3 is rotated in the stator 2, wherein in the discharge area 5, a pressure-volume area 11 and a suction-volume area 12 between the stator 2 and the rotor 3, due to the rotation of the rotor, lie opposite one another in a volume-changing and changing manner.
  • a discharge area 5 that closes on the pressure side and is attached to the end face 6 of the rotor 3 rotor head part 7 rotating with the rotor 3 is provided, which has at least one recess 8 which is continuous with the head part and which is introduced into the rotor head part 7 in relation to the holding rotor end face 6 in such a way that the recess 8 which rotates in the conveying direction 10 in conformity with the rotor 3 withstands the pressure Accompanying volume area 11 Opens and that a recess-free rotor head portion 13 keeps the opposite suction volume area 12 sealed during the opening period of the pressure volume area 11.
  • the rotor head part 7 is preferably designed as a perforated rotor disk, flat on its rear surface 30 and with its rotor head part rear surface 30 by screwing, welding or the like. attached to the rotor end face 6 of the helical rotor 3, actually the rotor worm end face.
  • the rotor head part 7 is thus an integral part of the rotor 3 outside the stator 2.
  • the rotor perforated disk 7 can be attached with its disk rear surface 30 to the rotor end face 6 such that the central axis 33 of the rotor perforated disk 7 can preferably coincide with the center 28 of the rotor end surface 6, the central axis 33 only straight elongated.
  • the central axis 33 of the rotor head part 7 is displaced away from the center 28 of the rotor end face 6, then no centric straight elongation, but an eccentric cam path is traversed.
  • the front surface 9 and the rear surface 30 can also be oval-shaped, pear-shaped or egg-shaped in cross-section or the like. especially designed for material reduction his.
  • a material-reduced second rotor head part 27 (dashed) is inserted.
  • the recess 8 is designed in such a way that the suction volume area 12, 12 'always remains sealed and rotated during the rotor rotation and the pressure volume area 11, 11' is opened in a rotor-conforming manner.
  • the rotor perforated disk 7 in FIG. 1 preferably has, as a continuous recess 8, an elongated hole which is largely bean-shaped in cross section.
  • the elongated hole 8 is made directly to the side of the edge and expands in the radial direction on the end face 6 of the rotor 3 in the rotor perforated disk 7, the hole cross section on it being dimensioned in accordance with the pressure build-up in the pressure Volume area 11 and the discharge of the material to be conveyed out of the pressure volume area 11 by the rotating rotor 3 is predetermined.
  • the rotor 3 is designed in the form of a round thread screw (cord thread) with a high pitch and large thread depth and acts as a displacement material displacer and as a seal along the conveying path 14 from the suction-side input area 4 to the pressure-side discharge area 5 between the rotor 3 and the stator 2.
  • the stator 2 and holds axially one after the other and due to the pitch and the depth of the thread formed cavities 15, 16, 17 - a suction-side entry cavity 15, a central conveying cavity 16, a discharge-side discharge cavity 17 - the between the stator surface 18 and the rotor outer surface 19 Delivery chambers 20,21,22 by between see the stator 2 and the rotor 3 form sealing areas 23, 24, the material to be conveyed in the conveying chambers 20, 21, 22 when the rotor 3 is rotated in the cavities 15, 16, 17 of the stator 2 from the suction-side inlet area 4 to the discharge-side discharge area 5 is transported.
  • the rotor 3 moves the material to be conveyed in the axial direction 10 along the conveying path 14 and at the same time in the radial direction with respect to the pump central axis 26 alternately in the discharge cavity 17 via the feeding conveying chambers 20, 21, 22 provided for this purpose, which form and opposing volume regions 11, 12, which are part of the discharge cavity 17 on the pressure side.
  • the rotor head part rear surface 30 and the stator end surface 25 are flat and each have an angle of approximately 90 ° to the pump central axis 26.
  • the rotor head part front surface 9 can be flat with respect to a disk-shaped configuration, but also spherical cap and / or with at least one wing or other projections having a profile for improving throughput and mixing of the conveyed material.
  • the discharge-side discharge area 5 of the eccentric screw pump 1 comprises the last section of the eccentric screw pump 1 that delivers the material to be conveyed, while the suction-side input area 4 represents the first section of the eccentric screw pump 1 that receives the material to be conveyed.
  • the invention thus makes it possible for the material to be conveyed out of the eccentric screw pump 1 on the discharge side after the rotor-rotation-related opening of the pressure volume region 5 and the sealing of the suction volume region 12 no longer to flow back through the hole-free disk part 13 and not to the rotor 3 pushed or rotated by the rotor 3. can suck in the conveyed material.
  • the hole 8 allows the material to be conveyed to flow through it without substantial resistance, while a backflow of the material to be conveyed in the direction of the suction volume region 12 is blocked through the hole-free disk part 13.
  • a pressure tube 34 which faces the rotor head part front surface 9 and via which the conveyed material is conveyed, can be fastened to the stator end face 25.
  • the pressure tube 34 can be locked in a sealed manner on the stator 2 by means of at least one holding element (not shown) that preferably surrounds the stator and pressure tube.
  • the rotor 3 is in the suction volume area 12 with its circular rotor end face 6 at an angular and rotational position 28, in which the rotor angle ⁇ e.g. is set to 0 °.
  • the perforated rotor disk 8 is attached to the rotor end face 6 in such a way that the bean-shaped elongated hole 8 begins with its hole start area 35 to a very small part of its effective opening cross section to cover the pressure volume area 11. Compliant with the pressure generated by the rotating rotor 3 in the pressure volume range
  • the cross-sectionally elongated hole size of the opening coverage of the pressure volume region 11 also becomes larger.
  • the remaining and hole-free disk part 13 can close off a part of the remaining pressure volume area 11 and the suction volume area
  • the rotor 3 has rotated through an angle ⁇ of 90 ° into the center position 28 ', as a result of which the bean-shaped elongated hole 8, including the hole start area 35 and the hole end area 36, has the largest part of the pressure volume area 11 in terms of hole cross section covered and thus opened it and the hole-free disk part 13 still seals the suction volume area 12.
  • the hole 8 with its hole end area 36 emerges from the reduced pressure volume area 11.
  • the original suction volume area 12 is still sealed off by the hole-free disk part 13, but is opened as a result of the rotor rotation as the pressure volume area 11 ', as in FIG.
  • the hole 8 enters with its hole start area 35 into the opposing pressure volume area 11 'which is building up.
  • FIG. 4 also shows that the hole 8 can be designed as a continuous recess in a different configuration in the form of a radially directed sector-section-shaped through opening 32 or sector-like recess 31 starting from the holding rotor end face 6, each of which is dashed.
  • the rotor perforated disk 7 shown in FIGS. 2, 3, 4 in front view for reducing the pressure at least on the sealing area 24 within the eccentric screw pump 1 has such circumferential dimensions that the stator opening 27 always rotates the suction volume area that arises when the rotor perforated disk 7 rotates 12 keeps sealed.
  • the eccentric screw pump 1 is shown schematically as an abbreviated longitudinal section along the line II in FIG. 3.
  • the rotor perforated disk 7 is dimensioned in such a way that its range of motion during rotor rotation preferably remains within the stator casing 29, ie does not move beyond the stator casing 29.
  • the rotor perforated disk 7 is firmly connected to the rotor end face 6 on its rear disk surface 30.
  • the disk rear surface 30 is flat in the hole-free region 13 such that it lies tightly against the stator end face 25, which is also preferably flat, and forms an angle of approximately 90 ° with the pump center axis 26.
  • the hole 8 opens the passage of the conveyed material to the downstream pressure pipe 26 to the pressure volume region 11.
  • the hole-free disk part 13 keeps the suction volume part 12 of the discharge cavity 17 on the pressure side closed.
  • FIG. 5 according to the invention, in a minimally short design of the stator 2, only one sealing area 24 of a worm gear can be formed, wherein the suction-side input area 4 can be followed directly by a discharge-side discharge area 5.
  • the position of the rotor 3 in the worm gear is stabilized by the rotor head part 7 resting on the stator face 25.
  • the eccentric screw pump 1 works as follows:
  • the metallic rotor 3 rotates in the stator 2 (worm shell) consisting of elastic material and seals the delivery chambers 20, 21, 22 on the inner surface of the stator 18.
  • the rotation of the rotor 3 moves the material to be conveyed in the conveying chambers 20, 21, 22 from the suction-side input region 4 to the discharge-side discharge region 5. This results in a continuous flow of material to be conveyed in the stator 2, which pulsatingly leaves the hole 8 of the rotor head part 7.
  • the material to be conveyed is reduced within the decreasing volume area 11 by the rotor rotation in the pressure Volume area 11 positioned hole 8 pressed through, while the suction volume area 12 remains closed.
  • the rotor end face 6 reaches a position 28 ′′ in which the decreasing pressure volume region 11 changes into a pressure volume region 11 ′ that is completely soaked up with the material to be conveyed, which previously was the Suction volume area 12 has been. Due to the rotor rotation beyond a rotor angle ⁇ of 180 °, the pressure is built up in the resulting pressure volume area 11 ′, which presses the material to be conveyed out of the hole 8 in a rotor-conforming manner. The previous pressure volume range 11 merges into the newly created suction volume range 12 'due to the rotor rotation.
  • the previously opened pressure volume area 11 is closed by the hole-free disk part 13 and built up to the suction volume area 12 '.
  • the sealing areas 24, 23, in particular the last sealing area 24 of the discharge cavity 17 on the pressure side are also not subjected to back pressure.
  • the increasing suction volume area 12 ′ exerts a strong suction effect on the following material to be conveyed from the conveying chamber 21.
  • the rotor perforated disk 7 results in a change of pumping processes and suction processes of the conveyed material within the discharge cavity 17, whereby the suction of the conveyed material into the in each case disc-closed volume regions 12 or 12 ', a higher degree of filling of conveyed goods is achieved there.
  • the invention enables the conveyor path 14 to be shortened and to be able to relate to two “cavity lengths” or to a “single-cavity-cavity-discharge-cavity” arrangement 15-16-17.
  • the conveyor section 14 can be shortened to a worm gear of the stator 2.
  • the required drive power can be achieved by means of a motor which is also reduced in power, whereby thus energy and material can also be saved.
  • An increase in the delivery pressure is fundamentally achieved by an increase in the pretension between the stator 2 and the rotor 3, which in a conventional manner usually has an axial surface e.g. by means of a clamping jacket comprising the stator 2.
  • One problem is that this involves a correspondingly increased energy expenditure for pump operation.
  • a corresponding increase in preload in the radial direction to the pump center axis 26 is provided with the least possible axial shape.
  • a radial cross-sectional taper can optionally be provided in the regions of the stator 2, preferably in integer intervals of a screw casing thread corresponding to one revolution, from the rotor end face 6.
  • a radial cross-sectional tapering element (not shown) can be assigned to the stator 2 at a distance from the rotor end face 6 corresponding to a worm shell thread of the stator 2.
  • the radial cross-sectional tapering element can be configured and arranged in the manner of a sleeve inside and / or outside of the stator casing 29, which can be changed in the radial direction, either in a controllable manner or via actuators, and with which the radial prestressing of the sealing areas 23, 24 of the stator 2 with respect to that Rotor 3 can be adjusted either step by step or continuously depending on the specified delivery pressure.
  • the invention opens up the possibility that, in addition to the time delay in the formation of wear, the manufacturing costs can also be reduced compared to the complicated designs of known re-tensionable and non-re-tensionable eccentric screw pumps and known check valve devices at the stator end area of eccentric screw pumps.
  • stator jacket rotor head part rear surface Sector-like recess Sector section-shaped through opening rotor head part center axis pressure pipe hole start area hole end area second rotor head part

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to an eccentric screw pump (1) comprising a stator (2) and a rotor (3) between which the material, which is to be transported, is displaced when the rotor (3) is rotated in the stator (2) from an inlet area (4) on the suction side to a discharge area (5) on the pressure side. Said pump comprises a rotor head part (7) which closes the pressure-side discharge area (5) and which is fixed to the front (6) of the rotor (3), rotating therewith. Said rotor head part comprises at least one recess (8) which transverses the head part and which is disposed in the rotor head part (7) in relation to the rotor surface (6) which is to be maintained, such that the recess (8), which rotates at the same time as the rotor (3) in the direction of conveyance (10), opens up the pressure volume area (11, 11') and a recess-free rotor head part area (13) keeps the opposite-lying suction volume area (12, 12') sealed while the pressure volume area (12, 12') is opened.

Description

Beschreibungdescription
ExzenterschneckenpumpeCavity Pump
Die Erfindung betrifft eine Exzenterschneckenpumpe, die einen Stator und einen Rotor aufweist, zwischen denen das Fördergut beim Drehen des Rotors im Stator von einem saugseitigen Eingangsbereich zu einem druckseitigen Austragsbereich verschoben wird, wobei sich im druckseitigen Austragsbereich ein Druck- Volumenbereich und ein Saug-Volumenbereich zwischen dem Stator und dem Rotor rotordrehungsbedingt sich ändernd und wechselnd gegenüberliegen. Derartige bekannte Exzenterschneckenpumpen enthalten einen als Schnecke ausgebildeten Rotor, der die Form einer Rundgewindeschraube mit hoher Steigung und großer Gewindetiefe hat, und einen Stator, der eine gewindeartige Innenstruktur aufweist und somit die Form eines Schneckenmantels hat. Dabei bildet der Stator durch seine gewindeartige Innenstruktur von der Saugseite aus zur Druckseite gerichtet axial nacheinander ausgebildete Hohlräume aus, in denen sich der Rotor dreht. Teile der Innenfläche des Stators und Teile der Außenfläche des Ro- tors berühren sich während der Drehung des Rotors, wobei zwischen der Statorinnenfläche und der Rotoraußenfläche Förderkammern und zugehörige Abdichtungsbereiche vorhanden sind, wobei das Fördergut in den Förderkammern beim Drehen des Rotors in den Hohlräumen des Stators von der Saugseite zur Druckseite entlang einer Förderstrecke verschoben wird.The invention relates to an eccentric screw pump, which has a stator and a rotor, between which the material to be conveyed is shifted from a suction-side input area to a pressure-side discharge area when the rotor is rotated in the stator, a pressure-volume area and a suction-volume area being located in the pressure-side discharge area the stator and the rotor are opposite and changing due to rotor rotation. Known eccentric screw pumps of this type contain a rotor designed as a screw, which has the shape of a round thread screw with a high pitch and a large thread depth, and a stator, which has a thread-like inner structure and thus has the shape of a screw shell. The thread-like inner structure of the stator, from the suction side to the pressure side, forms cavities which are formed axially one after the other and in which the rotor rotates. Parts of the inner surface of the stator and parts of the outer surface of the rotor touch during the rotation of the rotor, with conveying chambers and associated sealing areas being present between the inner surface of the stator and the outer surface of the rotor, the material to be conveyed in the conveying chambers when the rotor is rotating in the cavities of the stator is shifted from the suction side to the pressure side along a conveyor line.
Eine solche Exzenterschneckenpumpe ist aus der Druckschrift EP 0 713 974 bekannt, bei der durch das Drehen des Rotors in den Hohlräumen des Stators eine kontinuierliche Förderung von ab- rasivem Fördergut möglich ist. Der Stator ist dabei aus elastischem Material und liegt mit einer Vorspannung am Rotor an, wodurch am laufenden Kammerende stets eine Abdichtung entsteht. Das aus dem druckseitigen Austragshohlraum herausge- presste Fördergut drückt bedingt durch das im weiterführenden Druckrohr vorhandene Fördergut als gegensätzlicher Außendruck auf das rückwärtige nachgeschobene Fördergut. Der Förderpro- zess baut somit einen Innendruck, insbesondere gegen die Abdichtungsbereiche auf. Je höher der aufgebaute Außendruck im Druckrohr ist, um so größer muss die Vorspannung zwischen dem Rotor und dem Stator sein, um ein sicheres Abdichten zu gewährleisten. Ein Problem besteht darin, dass der Rotor und der Stator insbesondere während der Förderung des Förderguts einem Verschleiß unterliegen. Im Wesentlichen tritt der Verschleiß an den als Abdichtungen der Hohlräume ausgebildeten Ganghöhen des Stators von der Seite des druckseitigen Austragsbereichs ausgehend in Richtung zum saugseitigen Eingangsbereich auf. Die Verschleißzunahme bedingt die Abnahme der Förderleistung der Exzenterschneckenpumpe.Such an eccentric screw pump is known from document EP 0 713 974, in which continuous rotation of abrasive material to be conveyed is possible by rotating the rotor in the cavities of the stator. The stator is made of elastic material and bears against the rotor with a preload, which always creates a seal at the running chamber end. The material to be conveyed pressed out of the discharge cavity on the pressure side, due to the material to be conveyed in the downstream pressure pipe, presses on the rearward conveyed material as opposing external pressure. The conveying process thus builds up internal pressure, particularly against the sealing areas. The higher the external pressure built up in the pressure pipe, the greater the preload between the rotor and the stator in order to ensure a secure seal. One problem is that the rotor and the stator are subject to wear, particularly during the conveying of the conveyed material. Essentially, the wear occurs at the aisles of the stator designed as seals of the cavities, starting from the side of the discharge-side discharge area in the direction of the inlet-side entry area. The increase in wear causes the decrease in the delivery rate of the eccentric screw pump.
Der elastische Stator liegt mit einer Vorspannung am Rotor an, wobei es durch das Fördergut zu einem hohen Verschleiß zwischen Stator und Rotor kommen kann, der mit zunehmendem Druck äquivalent steigt. Der Verschleiß wandert progressiv von der Druck- zur Saugseite und hebt die ursprünglichen Abdichtungs- bereiche auf. Wenn der Innendruck den Außendruck nicht mehr überwinden kann, erfolgt schließlich ein Abbruch des Förderprozesses.The elastic stator rests on the rotor with a pre-tension, whereby the material being conveyed can cause high wear between the stator and the rotor, which increases with increasing pressure. The wear progressively moves from the pressure to the suction side and removes the original sealing areas. If the internal pressure can no longer overcome the external pressure, the conveying process is finally stopped.
Der druckorientierte Transport des Fördergutes in den Förder- kammern ist demzufolge in hohem Maße abhängig von der Beherrschung der Abdichtung in den Abdichtungsbereichen zwischen Rotor und Stator. Um die Probleme des störenden Verschleisses in den Abdichtungsbereichen zwischen der Rotoraußenfläche und der Statorinnenfläche über eine längere Betriebszeit zu beherr- sehen, sind Exzenterschneckenpumpen mit nachspannbaren Statoren bekannt, bei denen statorintegrierte Spannleisten vorgesehen sind bzw. an denen umschließbare Spanneinrichtungen manuell eingesetzt werden können. Mit den Spanneinrichtungen können bei erkennbarem Verschleiß an den inneren Abdichtungsbe- reichen im Detail bzw. je nach Bedarf im Ganzen radiale Kompressionen des Stators und damit eine Annäherung der Statorinnenfläche an die Rotoraußenfläche vorgenommen werden, wobei die Annäherung zu einer Herstellung der ursprünglichen Abdichtung in den Abdichtungsbereichen führen soll.The pressure-oriented transport of the material to be conveyed in the conveying chambers is therefore highly dependent on the mastery of the seal in the sealing areas between the rotor and stator. Eccentric screw pumps with re-tensionable stators are known in which stator-integrated tensioning strips are provided or on which enclosing tensioning devices can be used manually in order to control the problems of disruptive wear in the sealing areas between the rotor outer surface and the stator inner surface over a longer operating time. If the wear on the inner sealing areas is noticeable, the clamping devices can be used to make radial compressions of the stator in detail or, as required, as a whole, and thus to bring the inner surface of the stator closer to the outer surface of the rotor, whereby the approximation should lead to the creation of the original seal in the sealing areas.
Es sind des Weiteren in der Druckschrift DE 33 04 751 C2 Ex- zenterschneckenpumpen mit nicht nachspannbaren Statoren beschrieben, bei denen entweder der Stator konisch von der Saugseite zur Druckseite bei radial gleichartig dimensioniertem Rotor verengt oder der Rotor von der Saugseite zur Druckseite gerichtet einen zunehmenden Windungsquerschnitt bei durchweg gleichdimensioniertem Stator aufweist.There are also described in the publication DE 33 04 751 C2 eccentric screw pumps with non-retensionable stators, in which either the stator narrows conically from the suction side to the pressure side with a rotor of the same dimension or the rotor directed from the suction side to the pressure side has an increasing winding cross section with a uniformly dimensioned stator.
Ein Problem besteht darin, dass die Produktion und die Qualitätsüberwachung bei beiden Möglichkeiten und auch bei einer Kombination beider Möglichkeiten 'der Abdichtungskonstanthal- tung mit einem hohen Material-, Überwachungs- und damit Personalaufwand verbunden sind.One problem is that the production and the quality monitoring with both possibilities and also with a combination of both possibilities of keeping the seal constant are associated with a high expenditure of material, monitoring and thus personnel.
Es ist auch eine Exzenterschneckenpumpe aus der Druckschrift DE 202 15 849.7 bekannt, bei der am druckseitigen Austragsbe- reich eine das Fördergut passieren lassende Rückschlagventileinrichtung vorhanden ist, zu der eine an der endseitigen Fläche des Stators starr befestigte Verschlussscheibe gehört. Der Rotor dreht sich mit seiner Stirnfläche an der Verschlussscheibe, wodurch eine Abdichtung der wechselnden Druck- und Saug-Volumenbereiche erreicht werden soll. Die statorbefestigte Verschlussscheibe weist für den Austrag des Fördergutes zwei stationäre Durchgangsöffnungen auf, denen jeweils ein Rückschlagventil zugeordnet ist. Die beiden ventilbeschlagenen Durchgangsöffnungen sind den vom Austragsbereich des Rotors belegten Druck-Volumenbereich und Saug-Volumenbereich zugeordnet und werden geöffnet, wenn der Innendruck in den jeweiligen Volumenbereichen zwischen dem Stator und dem Rotor größer als der am Ventil anliegende Außendruck im Fördergut weiterleitenden Druckrohr ist.An eccentric screw pump is also known from the document DE 202 15 849.7, in which a check valve device which allows the material to be conveyed is present on the discharge-side discharge area and which includes a closure disk rigidly attached to the end face of the stator. The end face of the rotor rotates on the sealing disc, which is intended to seal the changing pressure and suction volume ranges. The stator-attached sealing disc has two stationary through openings for the discharge of the conveyed material, each of which is assigned a check valve. The two valve-fitted through openings are assigned to the pressure volume area and suction volume area occupied by the discharge area of the rotor and are opened when the internal pressure in the respective volume areas between the stator and the rotor is greater than is the pressure pipe passing on the valve in the conveyed material.
Ein Problem besteht darin, dass die Ausbildung der statorbefe- stigten Verschlussscheibe mit den Ventilen zusätzlicher Bauelemente bedarf. Die Ventile müssen nach Anwendungen der Exzenterschneckenpumpe zumindest gereinigt werden.One problem is that the design of the stator-fastened closure disk with the valves requires additional components. The valves must at least be cleaned after the eccentric screw pump has been used.
Der Erfindung liegt die Aufgabe zugrunde, eine Exzenterschnek- kenpumpe anzugeben, die im Bereich des Austrags in montageeinfacher und wartungsverbesserter Weise ausgebildet ist. Gleichzeitig soll der Verschleiß in den Abdichtungsbereichen von Stator und Rotor, insbesondere im Druckbereich des druckseitigen Austragshohlraums wesentlich verlangsamt bzw. weitgehend verringert werden. Dabei sollen auch die schon kurzen Längen des Stators und des Rotors bzw. der Förderstrecke weiter verkürzt werden und die ursprüngliche Förderleistung über längere Zeitdauer weitgehend erhalten bleiben.The invention is based on the object of specifying an eccentric screw pump which is designed in the area of the discharge in a manner which is simple to install and improves maintenance. At the same time, the wear in the sealing areas of the stator and rotor, in particular in the pressure area of the discharge cavity on the pressure side, is to be substantially slowed down or largely reduced. The already short lengths of the stator and the rotor or the conveying path should also be further shortened and the original conveying capacity should be largely retained over a longer period of time.
Die Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst. In der Exzenterschneckenpumpe gemäß dem Oberbegriff des Patentanspruchs 1 ist ein den druckseitigen Austragsbereich abschließendes, an der Stirnfläche des Rotors befestigtes, sich mit dem Rotor drehendes Rotorkopfteil vorgesehen, das mindestens eine kopfteildurchgängige Ausnehmung aufweist, die in Bezug zur halternden Rotorstirnfläche derart in das Rotorkopfteil eingebracht ist, dass die sich mit dem Rotor in Förderrichtung konform drehende Ausnehmung den Druck-Volumenbereich begleitend öffnet und dass ein ausnehmungsfreier Rotorkopfteilbe- reich während der Öffnungsdauer des Druck-Volumenbereiches den gegenüberliegenden Saug-Volumenbereich abdichtend verschlossen hält. Die Befestigung des Rotorkopfteils ist an der Rotorstirnfläche durch Verschraubung, Verschweißung od.dgl. mit der Rotorkopf- teilrückflache herbeigeführt.The object is solved by the features of claim 1. In the eccentric screw pump according to the preamble of claim 1 there is provided a rotor head part which closes off the discharge-side discharge area and is fastened to the end face of the rotor and rotates with the rotor and has at least one recess through the head part which is introduced into the rotor head part in this way in relation to the holding rotor end face that the recess, which rotates in the conveying direction in conformity with the rotor, opens the pressure volume area and that a recess-free rotor head part area keeps the opposite suction volume area sealed in the opening period of the pressure volume area. The rotor head part is attached to the rotor end face by screwing, welding or the like. brought about with the back of the rotor head part.
Das Rotorkopfteil kann dabei an der Rotorstirnfläche derart befestigt sein, dass die Mittelachse des Rotorkopfteils mit dem Mittelpunkt der Rotorstirnfläche übereinstimmen kann. Dann stellt die Bewegung der Mittelpunktachse eine zentrische ge- radlinige Elongation dar, bei keiner Übereinstimmung kann eine exzentrische Kurvenbahn durchlaufen werden.The rotor head part can be attached to the rotor end face in such a way that the central axis of the rotor head part can coincide with the center of the rotor end face. Then the movement of the center axis represents a centric straight-line elongation; if there is no match, an eccentric cam track can be run.
Die durchgängige Ausnehmung ist unmittelbar seitlich an der Stirnfläche des Rotors in dem Rotorkopfteil eingebracht, wobei der Ausnehmungsquerschnitt dimensionierungskonform mit dem Druckaufbau innerhalb des Druck-Volumenbereiches und dem Austrag des Fördergutes durch den sich drehenden Rotor vorgegeben ist.The continuous recess is made directly laterally on the end face of the rotor in the rotor head part, the recess cross section being specified in accordance with the dimensions with the pressure build-up within the pressure volume range and the discharge of the conveyed material by the rotating rotor.
Das Rotorkopfteil kann vorzugsweise eine Rotorlochscheibe mit kreisförmigen Flächen sein. Die zugehörige durchgängige Ausnehmung kann vorzugsweise ein im draufsichtigen Querschnitt weitgehend bohnenförmiges Langloch darstellen. Das Rotorkopfteil ist dabei derart an der Rotorstirnfläche an- gebracht, dass das Loch vom Rand der halternden Rotorstirnfläche in radialer Richtung ausgehend mit seinem wirksamen Öffnungsquerschnitt rotorkonform mit der Druckerzeugung innerhalb des Druck-Volumenbereiches mit dem Lochanfangsbereich in den Druck-Volumenbereich eintritt und später mit dem Lochendebe- reich aus dem Druck-Volumenbereich wieder austritt. Die durchgängige Ausnehmung des Rotorkopfteils kann wahlweise auch als eine vom Rand der halternden Rotorstirnfläche ausgehende, radial gerichtete sektorabschnittsförmige Durchgangsöffnung oder sektorartige Aussparung ausgebildet sein, die wie bei der Langlochausbildung mit ihrem jeweils wirksamen Öffnungsquerschnitt rotorkonform mit der Druckerzeugung innerhalb des Druck-Volumenbereiches durch den Rotor in den Druck- Volumenbereich eintritt und nach Überstreichung des Druck- Volumenbereiches aus dem Druck-Volumenbereich wieder austritt.The rotor head part can preferably be a perforated rotor disk with circular surfaces. The associated continuous recess can preferably be an elongated hole which is largely bean-shaped in plan cross section. The rotor head part is attached to the rotor end face in such a way that the hole, starting from the edge of the holding rotor end face in the radial direction with its effective opening cross section, enters the pressure volume area with the hole beginning area and later with the pressure generation within the pressure volume area with the hole beginning area Hole end area emerges from the pressure volume area again. The continuous recess of the rotor head part can optionally also be designed as a radially directed sector-section-shaped through opening or sector-like recess starting from the edge of the holding rotor end face, which, like in the case of the elongated hole design with its respectively effective opening cross section, conforms to the rotor with the generation of pressure within the pressure volume range by the rotor the pressure volume area enters and exits the pressure volume area after the pressure volume area has been crossed.
Das Rotorkopfteil weist zur Druckminderung auf die Abdichtungsbereiche innerhalb des Stators derartige Umfangs- Dimensionierungen auf, dass das Rotorkopfteil mit seinem restlichen ausnehmungsfreien Rotorkopfteilbereich den jeweils bei der Drehung entstehenden Saug-Volumenbereich im Bereich der Statoröffnung verschlossen hält.To reduce pressure on the sealing areas within the stator, the rotor head part has such circumferential dimensions that the rotor head part with its remaining, recess-free rotor head part area keeps the suction volume area in the area of the stator opening that is created during rotation closed.
Der Rotor kann als Schnecke in Form einer Rundgewindeschraube mit hoher Steigung und großer Gewindetiefe ausgebildet sein, wobei der Stator einen Schneckenmantel darstellt und axial nacheinander ausgebildete Hohlräume - zumindest einen saugseitigen Eintragshohlraum und einen druckseitigen Austragshohl- raum - einer Förderstrecke enthält, wobei sich zwischen der Statorinnenfläche und der Rotoraußenfläche Förderkammern durch zwischen dem Stator und dem Rotor angepasste Abdichtungsbereiche ausbilden, wobei das Fördergut in den Förderkammern beim Drehen des Rotors in den Hohlräumen des Stators vom saugseitigen Eingangsbereich zum druckseitigen Austragsbereich verschiebbar ist.The rotor can be designed as a worm in the form of a round-thread screw with a high pitch and large thread depth, the stator representing a worm shell and cavities formed axially one after the other - at least one suction-side entry cavity and one pressure-side discharge cavity - containing a conveying path, with the stator inner surface and the rotor outer surface form conveying chambers by sealing areas adapted between the stator and the rotor, the material to be conveyed in the conveying chambers being displaceable from the suction-side input area to the pressure-side discharge area when the rotor is rotated in the cavities of the stator.
An die Statorstirnfläche ist ein Druckrohr anschließbar, über das das Fördergut weitergeleitet wird, wobei das Druckrohr mittels mindestens eines stator- und druckrohrumfassenden Halterungselementes abgedichtet am Stator arretierbar ist.A pressure pipe can be connected to the stator face, via which the material to be conveyed is passed, the pressure pipe can be locked on the stator in a sealed manner by means of at least one holding element that surrounds the stator and pressure pipe.
Die Erfindung ermöglicht es, dass durch das Vorhandensein des Rotorkopfteils bzw. der Rotorlochscheibe am druckseitigen Austragsbereich eine Trennung des ursprünglichen druckrohrbezoge- nen Druckraumes nach dem Pumpenausgang vom ursprünglichen pumpenbezogenen druckseitigen Austragshohlraum erreicht wird. Nach der Öffnung des druckseitigen Austragsbereiches durch die jeweils rotorrotationsbedingte Öffnung mittels der durchgängigen Ausnehmung wird eine nachfolgende schonende Fördergutfüllung vom saugseitigen Eingangsbereich aus gerichtet durch den rotierenden Rotor erhalten.The invention makes it possible for the presence of the rotor head part or the rotor perforated disk on the discharge-side discharge region to separate the original pressure-tube-related pressure space after the pump outlet from the original pump-related discharge-side discharge cavity. After the discharge area on the pressure side has been opened through the opening, which is dependent on the rotor rotation, by means of the continuous recess, a subsequent gentle filling of the conveyed material is obtained from the suction-side entrance area and directed by the rotating rotor.
Weiterbildungen und weitere Ausgestaltungen sind in weiteren Unteransprüchen beschrieben.Further developments and further refinements are described in further subclaims.
Die Erfindung wird mittels eines Ausführungsbeispiels anhand von Zeichnungen näher erläutert.The invention is explained in more detail by means of an embodiment with reference to drawings.
Es zeigen:Show it:
Fig. 1 eine schematische perspektivische Explosionsdarstellung einer erfindungsgemäßen Exzenterschneckenpumpe mit einem von der Rotorstirnfläche gelösten Rotorkopf- teil und einem von der Statorstirnfläche gelösten anschließbaren Druckrohr,1 shows a schematic perspective exploded view of an eccentric screw pump according to the invention with a rotor head part detached from the rotor end face and a connectable pressure pipe detached from the stator end face,
Fig. 2 eine schematische stirnseitige Draufsicht auf eineFig. 2 is a schematic frontal plan view of a
Rotorlochscheibe mit einem Loch in einer Position zu Beginn des Austrags von Fördergut aus einem Druck-Perforated rotor disk with a hole in one position at the beginning of the discharge of conveyed material from a pressure
Volumenbereich bei einem festgelegten Rotor-Winkel α gleich 0' Fig. 3 eine schematische stirnseitige Draufsicht auf die Rotorlochscheibe mit dem Loch in einer Position bei maximalem Austrag von Fördergut aus dem Druck-Volumenbereich bei einer Drehung des Rotors um einen Rotor- Winkel gleich 90° nach Fig. 2,Volume range at a fixed rotor angle α equal to 0 ' 3 shows a schematic frontal top view of the perforated rotor disk with the hole in a position with maximum discharge of conveyed material from the pressure volume range when the rotor is rotated through a rotor angle equal to 90 ° according to FIG. 2,
Fig. 4 eine schematische stirnseitige Draufsicht auf die Rotorlochscheibe mit dem Loch in einer Position nach Ende des Austrage von Fördergut aus dem bisherigen Druck-Volumenbereich bzw. zu Beginn der Austrags vonFig. 4 is a schematic frontal top view of the perforated rotor disk with the hole in a position after the end of the discharge of conveyed material from the previous pressure volume range or at the beginning of the discharge of
Fördergut aus dem sich neu aufbauenden, gegenüberliegenden Druck-Volumenbereich bei einer Drehung des Rotors um einen Rotor-Winkel α gleich 180° nach Fig. 2 undConveyed material from the newly developing, opposite pressure volume range when the rotor is rotated by a rotor angle α equal to 180 ° according to FIGS. 2 and
Fig. 5 einen Längsschnitt durch eine verkürzte Exzenterschneckenpumpe mit der Rotorlochscheibe nach Fig. 3 längs der Linie I-I.5 shows a longitudinal section through a shortened eccentric screw pump with the rotor perforated disk according to FIG. 3 along the line I-I.
In Fig. 1 ist in einer schematischen Explosionsdarstellung eine Exzenterschneckenpumpe 1 gezeigt, die einen Stator 2 und einen Rotor 3 aufweist, zwischen denen das Fördergut beim Drehen des Rotors 3 im Stator 2 von einem saugseitigen Eingangsbereich 4 zu einem druckseitigen Austragsbereich 5 verschoben wird, wobei im Austragsbereich 5 ein Druck-Volumenbereich 11 und ein Saug-Volumenbereich 12 zwischen dem Stator 2 und dem Rotor 3 rotordrehungsbedingt sich volumenändernd und wechselnd gegenüberliegen.1 shows a schematic exploded view of an eccentric screw pump 1, which has a stator 2 and a rotor 3, between which the material to be conveyed is shifted from a suction-side input area 4 to a pressure-side discharge area 5 when the rotor 3 is rotated in the stator 2, wherein in the discharge area 5, a pressure-volume area 11 and a suction-volume area 12 between the stator 2 and the rotor 3, due to the rotation of the rotor, lie opposite one another in a volume-changing and changing manner.
Erfindungsgemäß ist ein den druckseitigen Austragsbereich 5 abschließendes, an der Stirnfläche 6 des Rotors 3 befestigtes, sich mit dem Rotor 3 drehendes Rotorkopfteil 7 vorgesehen, das mindestens eine kopfteildurchgängige Ausnehmung 8 aufweist, die in Bezug zur halternden Rotorstirnfläche 6 derart in das Rotorkopfteil 7 eingebracht ist, dass die sich mit dem Rotor 3 in Förderrichtung 10 konform drehende Ausnehmung 8 den Druck- Volumenbereich 11 begleitend Öffnet und dass ein ausnehmungs- freier Rotorkopfteilbereich 13 während der Öffnungsdauer des Druck-Volumenbereiches 11 den gegenüberliegenden Saug- Volumenbereich 12 abdichtend verschlossen hält.According to the invention, a discharge area 5 that closes on the pressure side and is attached to the end face 6 of the rotor 3 rotor head part 7 rotating with the rotor 3 is provided, which has at least one recess 8 which is continuous with the head part and which is introduced into the rotor head part 7 in relation to the holding rotor end face 6 in such a way that the recess 8 which rotates in the conveying direction 10 in conformity with the rotor 3 withstands the pressure Accompanying volume area 11 Opens and that a recess-free rotor head portion 13 keeps the opposite suction volume area 12 sealed during the opening period of the pressure volume area 11.
Das Rotorkopfteil 7 ist vorzugsweise als eine Rotorlochscheibe ausgebildet, an ihrer Rückfläche 30 ebenflächig und mit seiner Rotorkopfteilrückfläche 30 durch Verschraubung, Verschweißung od.dgl. an der Rotorstirnfläche 6 des schneckenförmigen Rotors 3, eigentlich der Rotorschneckenstirnfläche, befestigt. Das Rotorkopfteil 7 ist somit ein fester Bestandteil des Rotors 3 außerhalb des Stators 2.The rotor head part 7 is preferably designed as a perforated rotor disk, flat on its rear surface 30 and with its rotor head part rear surface 30 by screwing, welding or the like. attached to the rotor end face 6 of the helical rotor 3, actually the rotor worm end face. The rotor head part 7 is thus an integral part of the rotor 3 outside the stator 2.
Die Rotorlochscheibe 7 kann bei einer kreisförmigen Scheiben- frontfläche 9 und kreisförmigen Scheibenrückfläche 30 mit ihrer Scheibenrückfläche 30 derart an der Rotorstirnfläche 6 befestigt sein, dass die Mittelachse 33 der Rotorlochscheibe 7 vorzugsweise mit dem Mittelpunkt 28 der Rotorstirnfläche 6 übereinstimmen kann, wobei die Mittelachse 33 nur geradlinig elongiert. Ist aber die Mittelachse 33 des Rotorkopfteils 7 vom Mittelpunkt 28 der RotorStirnfläche 6 weg verlagert, dann wird keine zentrisch geradlinige Elongation, sondern eine exzentrische Kurvenbahn durchlaufen.With a circular disk front surface 9 and circular disk rear surface 30, the rotor perforated disk 7 can be attached with its disk rear surface 30 to the rotor end face 6 such that the central axis 33 of the rotor perforated disk 7 can preferably coincide with the center 28 of the rotor end surface 6, the central axis 33 only straight elongated. However, if the central axis 33 of the rotor head part 7 is displaced away from the center 28 of the rotor end face 6, then no centric straight elongation, but an eccentric cam path is traversed.
Die Frontfläche 9 und die Rückfläche 30 können umfangsbezogen aber auch ovalförmig, im Querschnitt birnenförmig oder eiförmig od.dgl. insbesondere zur Materialreduzierung ausgebildet sein. In Fig. 2 ist z.B. ein materialreduziertes zweites Rotorkopfteil 27 (gestrichelt) eingefügt.The front surface 9 and the rear surface 30 can also be oval-shaped, pear-shaped or egg-shaped in cross-section or the like. especially designed for material reduction his. In Fig. 2, for example, a material-reduced second rotor head part 27 (dashed) is inserted.
Wesentlich ist es, dass die Ausnehmung 8 derart ausgebildet ist, dass während der Rotordrehung der Saug-Volumenbereich 12,12' immer abgedichtet verschlossen bleibt und der Druck- Volumenbereich 11,11' rotorkonform geöffnet wird.It is essential that the recess 8 is designed in such a way that the suction volume area 12, 12 'always remains sealed and rotated during the rotor rotation and the pressure volume area 11, 11' is opened in a rotor-conforming manner.
Die Rotorlochscheibe 7 in Fig. 1 weist als eine durchgängige Ausnehmung 8 vorzugsweise ein im draufsiehtigen Querschnitt weitgehend bohnenförmiges Langloch auf.The rotor perforated disk 7 in FIG. 1 preferably has, as a continuous recess 8, an elongated hole which is largely bean-shaped in cross section.
Wie auch in den Fig. 2 bis 4 gezeigt, ist das Langloch 8 unmittelbar seitlich vom Rand ausgehend und in radialer Richtung sich ausdehnend an der Stirnfläche 6 des Rotors 3 in der Rotorlochscheibe 7 eingebracht, wobei der draufsiehtige Lochquerschnitt dimensionierungskonform mit dem Druckaufbau im Druck-Volumenbereich 11 und dem Austrag des Fördergutes aus dem Druck-Volumenbereich 11 heraus durch den sich drehenden Rotor 3 vorgegeben ist.As also shown in FIGS. 2 to 4, the elongated hole 8 is made directly to the side of the edge and expands in the radial direction on the end face 6 of the rotor 3 in the rotor perforated disk 7, the hole cross section on it being dimensioned in accordance with the pressure build-up in the pressure Volume area 11 and the discharge of the material to be conveyed out of the pressure volume area 11 by the rotating rotor 3 is predetermined.
Der Rotor 3 ist in Form einer Rundgewindeschraube (Kordelgewinde) mit hoher Steigung und großer Gewindetiefe ausgebildet und wirkt als Fördergutverdränger und als Abdichter längs der Förderstrecke 14 vom saugseitigen Eingangsbereich 4 zum druckseitigen Austragsbereich 5 zwischen dem Rotor 3 und dem Stator 2. Der Stator 2 u fasst axial nacheinander und durch die Steigung und die Tiefe des Gewindes bedingte ausgebildete Hohlräume 15,16,17 - einen saugseitigen Eintragshohlraum 15, einen mittleren Förderhohlraum 16, einen druckseitigen Austragshohl- raum 17 -, wobei sich zwischen der Statorinnenfläche 18 und der Rotoraußenfläche 19 die Förderkammern 20,21,22 durch zwi- sehen dem Stator 2 und dem Rotor 3 erzeugte Abdichtungsbereiche 23,24 ausbilden, wobei das Fördergut in den Förderkammern 20,21,22 beim Drehen des Rotors 3 in den Hohlräumen 15,16,17 des Stators 2 von dem saugseitigen Eingangsbereich 4 zum druckseitigen Austragsbereich 5 transportiert wird.The rotor 3 is designed in the form of a round thread screw (cord thread) with a high pitch and large thread depth and acts as a displacement material displacer and as a seal along the conveying path 14 from the suction-side input area 4 to the pressure-side discharge area 5 between the rotor 3 and the stator 2. The stator 2 and holds axially one after the other and due to the pitch and the depth of the thread formed cavities 15, 16, 17 - a suction-side entry cavity 15, a central conveying cavity 16, a discharge-side discharge cavity 17 - the between the stator surface 18 and the rotor outer surface 19 Delivery chambers 20,21,22 by between see the stator 2 and the rotor 3 form sealing areas 23, 24, the material to be conveyed in the conveying chambers 20, 21, 22 when the rotor 3 is rotated in the cavities 15, 16, 17 of the stator 2 from the suction-side inlet area 4 to the discharge-side discharge area 5 is transported.
Dabei verschiebt der Rotor 3 durch seine schneckenförmige Ausbildung das Fördergut in axialer Richtung 10 längs der Förderstrecke 14 und zugleich in radialer Richtung in Bezug auf die Pumpenmittelachse 26 wechselseitig im Austragshohlraum 17 über die nachschiebenden Förderkammern 20,21,22 in dafür vorgesehene, sich ausbildende und gegenüberliegende Volumenbereiche 11,12, die Teil des druckseitigen Austragshohlraums 17 sind.Due to its helical design, the rotor 3 moves the material to be conveyed in the axial direction 10 along the conveying path 14 and at the same time in the radial direction with respect to the pump central axis 26 alternately in the discharge cavity 17 via the feeding conveying chambers 20, 21, 22 provided for this purpose, which form and opposing volume regions 11, 12, which are part of the discharge cavity 17 on the pressure side.
Im Austragsbereich 5 des druckseitigen Austragshohlraums 17, der etwa einem "halben" mittleren Hohlraum 16, ähnlich der ersten, in Fig. 1 dargestellten Förderkammer 20 entspricht, befindet sich die das Fördergut durch die Ausnehmung 8 passieren lassende Rotorlochscheibe 7, die in Fig. 1 der besseren Erläu- terung wegen von der Rotorstirnfläche 6 in Explosionsdarstellung abgelöst ist und erfindungsgemäß bei Befestigung an der Rotorstirnfläche 6 an der Statorstirnfläche 25 abdichtend anliegt.In the discharge area 5 of the discharge cavity 17 on the pressure side, which corresponds approximately to a "half" central cavity 16, similar to the first conveying chamber 20 shown in FIG. 1, there is the perforated rotor disk 7 which allows the conveyed material to pass through the recess 8 and which is shown in FIG for the sake of better explanation, it has been detached from the rotor end face 6 in an exploded view and, according to the invention, lies sealingly against the stator end face 25 when it is fastened to the rotor end face 6.
Die Rotorkopfteilrückfläche 30 und die Statorstirnfläche 25 sind ebenflächig ausgebildet und weisen jeweils einen Winkel von ca. 90 ° zur Pumpenmittelachse 26 auf.The rotor head part rear surface 30 and the stator end surface 25 are flat and each have an angle of approximately 90 ° to the pump central axis 26.
Die Rotorkopfteilfrontflache 9 kann ebenflächig bezüglich ei- ner scheibenförmigen Ausbildung, aber auch kugelkalottenförmig und/oder mit mindestens einem Flügel oder anderen Vorsprüngen aufweisendem Profil zur Durchsatz- und Mischverbesserung des Fördergutes versehen sein.The rotor head part front surface 9 can be flat with respect to a disk-shaped configuration, but also spherical cap and / or with at least one wing or other projections having a profile for improving throughput and mixing of the conveyed material.
Der druckseitige Austragsbereich 5 der Exzenterschneckenpumpe 1 umfasst deren letzten, das Fördergut abgebenden Abschnitt der Exzenterschneckenpumpe 1, während der saugseitige Eingangsbereich 4 den ersten, das Fördergut aufnehmenden Abschnitt der Exzenterschneckenpumpe 1 darstellt .The discharge-side discharge area 5 of the eccentric screw pump 1 comprises the last section of the eccentric screw pump 1 that delivers the material to be conveyed, while the suction-side input area 4 represents the first section of the eccentric screw pump 1 that receives the material to be conveyed.
Die Erfindung ermöglicht es somit, dass das aus der Exzenterschneckenpumpe 1 austragsseitig herausgedrückte Fördergut nach der rotorrotationsbedingten Öffnung des Druck-Volumenbereiches 5 sowie der Abdichtung des Saug-Volumenbereiches 12 durch den lochfreien Scheibenteil 13 nicht mehr zurückströmen und nicht auf das vom Rotor 3 nachgeschobene bzw. nachgesaugte Fördergut drücken kann.The invention thus makes it possible for the material to be conveyed out of the eccentric screw pump 1 on the discharge side after the rotor-rotation-related opening of the pressure volume region 5 and the sealing of the suction volume region 12 no longer to flow back through the hole-free disk part 13 and not to the rotor 3 pushed or rotated by the rotor 3. can suck in the conveyed material.
Das Loch 8 lässt das Fördergut ohne wesentlichen Widerstand durch sich hindurchströmen, während eine Rückströmung des För- dergutes in Richtung zum Saug-Volumenbereich 12 durch den lochfreien Scheibenteil 13 hindurch versperrt wird.The hole 8 allows the material to be conveyed to flow through it without substantial resistance, while a backflow of the material to be conveyed in the direction of the suction volume region 12 is blocked through the hole-free disk part 13.
Damit erfolgt bei jeder Drehung des Rotors 3 zumindest eine Entlastung des zweiten und zugleich letzten Abdichtungsberei- ches 24 in den Bereichen des Stators 2 und des Rotors 3, wodurch eine Verschleißminderung eintritt.With each rotation of the rotor 3 there is at least relief of the second and at the same time the last sealing area 24 in the areas of the stator 2 and the rotor 3, whereby wear is reduced.
Auf die Statorstirnfläche 25 ist, wie in Fig. 1 gezeigt ist, ein der Rotorkopfteilfrontfläche 9 zugewendetes Druckrohr 34 befestigbar, über das das Fördergut weitergeleitet wird. Das Druckrohr 34 kann mittels mindestens eines vorzugsweise stator- und druckrohrumfassenden Halterungselementes (nicht eingezeichnet) abgedichtet am Stator 2 arretiert sein.As shown in FIG. 1, a pressure tube 34, which faces the rotor head part front surface 9 and via which the conveyed material is conveyed, can be fastened to the stator end face 25. The pressure tube 34 can be locked in a sealed manner on the stator 2 by means of at least one holding element (not shown) that preferably surrounds the stator and pressure tube.
In Fig. 2 befindet sich der Rotor 3 im Saug-Volumenbereich 12 mit seiner kreisförmigen Rotorstirnfläche 6 bei einer Winkel- und Rotationsstellung 28, bei der der Rotor-Winkel α z.B. gleich 0° festgelegt ist. Die Rotorlochscheibe 8 ist derart an der Rotorstirnfläche 6 angebracht, dass das bohnenförmige Langloch 8 mit seinem Lochanfangsbereich 35 zu einem sehr geringen Teil seines wirksamen Öffnungsquerschnitts beginnt, den Druck-Volumenbereich 11 zu überdecken. Konform mit der Druckerzeugung durch den drehenden Rotor 3 im Druck-VolumenbereichIn Fig. 2 the rotor 3 is in the suction volume area 12 with its circular rotor end face 6 at an angular and rotational position 28, in which the rotor angle α e.g. is set to 0 °. The perforated rotor disk 8 is attached to the rotor end face 6 in such a way that the bean-shaped elongated hole 8 begins with its hole start area 35 to a very small part of its effective opening cross section to cover the pressure volume area 11. Compliant with the pressure generated by the rotating rotor 3 in the pressure volume range
11 wird die querschnittswirksame Langlochgröße der Öffnungs- Überdeckung des Druck-Volumenbereiches 11 ebenfalls größer.11, the cross-sectionally elongated hole size of the opening coverage of the pressure volume region 11 also becomes larger.
Der restliche und lochfreie Scheibenteil 13 kann je nach Größe des Langloches 8 einen Teil des restlichen Druck- Volumenbereiches 11 verschließen sowie den Saug-VolumenbereichDepending on the size of the elongated hole 8, the remaining and hole-free disk part 13 can close off a part of the remaining pressure volume area 11 and the suction volume area
12 abdichtend verschließen. Die Lage der Rotorlochscheibe 7 zum Rotor 3 in Fig. 2 entspricht annähernd der Position der12 seal. The position of the perforated rotor disk 7 relative to the rotor 3 in FIG. 2 corresponds approximately to the position of the
Rotorlochscheibe 7 zum Stator 2 in Fig. 1.Rotor disk 7 to the stator 2 in Fig. 1st
In Fig. 3 hat sich der Rotor 3 um einen Winkel α von 90° in die Mittelpunkt-Stellung 28' gedreht, wodurch das bohnenförmi- ge Langloch 8 lochquerschnittsmäßig vollständig einschließlich des Lochanfangsbereiches 35 und des Lochendebereiches 36 den größten Teil des Druck-Volumenbereichs 11 überdeckt und diesen somit geöffnet hat und wobei der lochfreie Scheibenteil 13 immer noch den Saug-Volumenbereich 12 abgedichtet verschließt. In Fig. 4 ist der Austrag des Fördergutes aus dem Druck- Volumenbereich 11 durch Drehen des Rotors 3 um einen Rotor- Winkel α von weiteren 90°, d.h. insgesamt um 180°, in der Mittelpunkt-Stellung 28'' beendet. Dabei tritt das Loch 8 mit seinem Lochendebereich 36 aus dem abgebauten Druck- Volumenbereich 11 heraus. Der ursprüngliche Saug-Volumenbe- reich 12 ist durch das lochfreie Scheibenteil 13 immer noch abgedichtet verschlossen, wird aber infolge der Rotorrotation als Druck-Volumenbereich 11' wie in Fig. 2 rotordrehungskonform beginnend geöffnet. Das Loch 8 tritt mit seinem Lochanfangsbereich 35 in den sich aufbauenden gegenüberliegenden Druck-Volumenbereich 11' ein.3, the rotor 3 has rotated through an angle α of 90 ° into the center position 28 ', as a result of which the bean-shaped elongated hole 8, including the hole start area 35 and the hole end area 36, has the largest part of the pressure volume area 11 in terms of hole cross section covered and thus opened it and the hole-free disk part 13 still seals the suction volume area 12. 4, the discharge of the conveyed material from the pressure-volume region 11 by rotating the rotor 3 around a rotor Angle α of a further 90 °, ie a total of 180 °, ends in the center position 28 ″. The hole 8 with its hole end area 36 emerges from the reduced pressure volume area 11. The original suction volume area 12 is still sealed off by the hole-free disk part 13, but is opened as a result of the rotor rotation as the pressure volume area 11 ', as in FIG. The hole 8 enters with its hole start area 35 into the opposing pressure volume area 11 'which is building up.
In Fig. 4 ist auch dargestellt, dass das Loch 8 als eine durchgängige Ausnehmung in einer anderen Ausbildung in Form einer von der halternden Rotorstirnfläche 6 ausgehenden, radi- al gerichteten sektorabschnittsförmigen Durchgangsöffnung 32 oder sektorartigen Aussparung 31 ausgebildet sein kann, die jeweils gestrichelt sind.FIG. 4 also shows that the hole 8 can be designed as a continuous recess in a different configuration in the form of a radially directed sector-section-shaped through opening 32 or sector-like recess 31 starting from the holding rotor end face 6, each of which is dashed.
Die in den Fig. 2,3,4 in stirnseitiger Draufsicht dargestellte Rotorlochscheibe 7 zur Druckminderung zumindest auf den Abdichtungsbereich 24 innerhalb der Exzenterschneckenpumpe 1 weist solche Umfangs-Dimensionierungen auf, dass die Statoröffnung 27 bei Drehung der Rotorlochscheibe 7 immer den jeweils entstehenden Saug-Volumenbereich 12 abgedichtet ver- schlössen hält.The rotor perforated disk 7 shown in FIGS. 2, 3, 4 in front view for reducing the pressure at least on the sealing area 24 within the eccentric screw pump 1 has such circumferential dimensions that the stator opening 27 always rotates the suction volume area that arises when the rotor perforated disk 7 rotates 12 keeps sealed.
In Fig. 5 ist die Exzenterschneckenpumpe 1 als abgekürzter Längsschnitt längs der Linie I-I nach Fig. 3 schematisch dargestellt. Die Rotorlochscheibe 7 ist dabei derart dimensio- niert, dass sie in ihrem Bewegungsbereich bei der Rotorrotation vorzugsweise innerhalb des Statormantels 29 bleibt, d.h. sich nicht über den Statormantel 29 hinaus bewegt. Die Rotor- lochscheibe 7 ist an ihrer Scheibenrückfläche 30 mit der Rotorstirnfläche 6 fest verbunden. Die Scheibenrückfläche 30 ist im lochfreien Bereich 13 derart ebenflächig ausgebildet, dass sie an der ebenfalls vorzugsweise ebenflächigen Statorstirn- fläche 25 dicht anliegt und zur Pumpenmittelachse 26 einen Winkel von ca. 90° bildet. Das Loch 8 öffnet dem Druck- Volumenbereich 11 den Durchgang des Fördergutes zum nachfolgenden Druckrohr 26. Der lochfreie Scheibenteil 13 hält den Saug-Volumenteil 12 des druckseitigen Austragshohlraums 17 verschlossen.5, the eccentric screw pump 1 is shown schematically as an abbreviated longitudinal section along the line II in FIG. 3. The rotor perforated disk 7 is dimensioned in such a way that its range of motion during rotor rotation preferably remains within the stator casing 29, ie does not move beyond the stator casing 29. The rotor perforated disk 7 is firmly connected to the rotor end face 6 on its rear disk surface 30. The disk rear surface 30 is flat in the hole-free region 13 such that it lies tightly against the stator end face 25, which is also preferably flat, and forms an angle of approximately 90 ° with the pump center axis 26. The hole 8 opens the passage of the conveyed material to the downstream pressure pipe 26 to the pressure volume region 11. The hole-free disk part 13 keeps the suction volume part 12 of the discharge cavity 17 on the pressure side closed.
In Fig. 5 kann erfindungsbedingt in einer minimal kurzen Ausbildung des Stators 2 nur ein Abdichtungsbereich 24 eines Schneckenganges ausgebildet sein, wobei sich dem saugseitigen Eingangsbereich 4 unmittelbar ein druckseitiger Austragsbe- reich 5 anschließen kann. Die Lagestabilisierung des Rotors 3 im Schneckengang ist durch das an der Statorstirnfläche 25 anliegenden Rotorkopfteil 7 gegeben.In FIG. 5, according to the invention, in a minimally short design of the stator 2, only one sealing area 24 of a worm gear can be formed, wherein the suction-side input area 4 can be followed directly by a discharge-side discharge area 5. The position of the rotor 3 in the worm gear is stabilized by the rotor head part 7 resting on the stator face 25.
Die Funktionsweise der erfindungsgemäßen Exzenterschneckenpum- pe 1 erfolgt folgendermaßen:The eccentric screw pump 1 according to the invention works as follows:
Der metallische Rotor 3 (Schnecke) rotiert in dem aus elastischem Material bestehenden Stator 2 (Schneckenmantel) und dichtet die Förderkammern 20,21,22 an der Statorinnenfläche 18 ab. Durch die Drehung des Rotors 3 wird das Fördergut in den Förderkammern 20,21,22 von dem saugseitigen Eingangsbereich 4 zum druckseitigen Austragsbereich 5 verschoben. Es ergibt sich dabei im Stator 2 ein kontinuierlicher Fördergutstrom, der das Loch 8 des Rotorkopfteils 7 pulsierend verlässt. Wird der Fördergutstrom in den druckseitigen Austragshohlraum 17 verschoben, insbesondere über die Förderkammer 22, wird das Fördergut innerhalb des sich verkleinernden Volumenbereiches 11 durch das jeweils durch die Rotorrotation im Druck- Volumenbereich 11 positionierte Loch 8 hindurch gepresst, während der Saug-Volumenbereich 12 verschlossen bleibt.The metallic rotor 3 (worm) rotates in the stator 2 (worm shell) consisting of elastic material and seals the delivery chambers 20, 21, 22 on the inner surface of the stator 18. The rotation of the rotor 3 moves the material to be conveyed in the conveying chambers 20, 21, 22 from the suction-side input region 4 to the discharge-side discharge region 5. This results in a continuous flow of material to be conveyed in the stator 2, which pulsatingly leaves the hole 8 of the rotor head part 7. If the flow of material to be conveyed is shifted into the discharge cavity 17 on the pressure side, in particular via the conveying chamber 22, the material to be conveyed is reduced within the decreasing volume area 11 by the rotor rotation in the pressure Volume area 11 positioned hole 8 pressed through, while the suction volume area 12 remains closed.
Zum Ende des Austragsvorgangs, der durch eine weitere Rotorro- tation erfolgt, erreicht die Rotorstirnfläche 6 eine Position 28'', in der der sich verkleinernde Druck-Volumenbereich 11 überwechselt in einen sich vollständig mit Fördergut vollgesaugten Druck-Volumenbereich 11', der bisher der Saug- Volumenbereich 12 gewesen ist. Durch die Rotorrotation über einen Rotor-Winkel α von 180° hinaus wird der Druck im entstehenden Druck-Volumenbereich 11' aufgebaut, der das Fördergut aus dem Loch 8 rotorkonform herauspresst . Der bisherige Druck-Volumenbereich 11 geht rotorrotationsbedingt in den neu entstehenden Saug-Volumenbereich 12' über. Danach wird der bisher geöffnete Druck-Volumenbereich 11 durch den lochfreien Scheibenteil 13 geschlossen und zum Saug-Volumenbereich 12' aufgebaut. Damit kann sich kein Rückdruck auf das in der nachfolgenden Förderkammer 21 befindliche Fördergut aufbauen und auch die Abdichtungsbereiche 24,23, insbesondere der letzte Abdichtungsbereich 24 des druckseitigen Austragshohlraums 17 werden nicht rückdruckbelastet . Im Gegenteil wird durch den sich vergrößernden Saug-Volumenbereich 12 ' eine starke Saugwirkung auf das nachfolgende Fördergut aus der Förderkammer 21 ausgeübt.At the end of the discharge process, which takes place by means of a further rotor rotation, the rotor end face 6 reaches a position 28 ″ in which the decreasing pressure volume region 11 changes into a pressure volume region 11 ′ that is completely soaked up with the material to be conveyed, which previously was the Suction volume area 12 has been. Due to the rotor rotation beyond a rotor angle α of 180 °, the pressure is built up in the resulting pressure volume area 11 ′, which presses the material to be conveyed out of the hole 8 in a rotor-conforming manner. The previous pressure volume range 11 merges into the newly created suction volume range 12 'due to the rotor rotation. Then the previously opened pressure volume area 11 is closed by the hole-free disk part 13 and built up to the suction volume area 12 '. As a result, no back pressure can build up on the material to be conveyed located in the downstream conveying chamber 21, and the sealing areas 24, 23, in particular the last sealing area 24 of the discharge cavity 17 on the pressure side, are also not subjected to back pressure. On the contrary, the increasing suction volume area 12 ′ exerts a strong suction effect on the following material to be conveyed from the conveying chamber 21.
Bedingt durch den jeweiligen Wechsel des Rotors 3 in die beiden extremen Lagepositionen 28,28'' der radial sich gegenüberliegenden Volumenbereiche 11,12 bzw. 12 ',11' innerhalb des druckseitigen Austragshohlraumes 17 entsteht durch die erfin- dungsgemäße Rotorlochscheibe 7 ein Wechsel von Pumpvorgängen und Ansaugvorgängen des Fördergutes innerhalb des Austragshohlraums 17, wobei durch das Ansaugen des Fördergutes in die jeweils scheibenverschlossenen Volumenbereiche 12 oder 12' hinein dort ein höherer Füllungsgrad an Fördergut erreicht wird.Due to the respective change of the rotor 3 into the two extreme position positions 28, 28 ″ of the radially opposite volume regions 11, 12 and 12 ′, 11 ′ within the discharge cavity 17 on the pressure side, the rotor perforated disk 7 according to the invention results in a change of pumping processes and suction processes of the conveyed material within the discharge cavity 17, whereby the suction of the conveyed material into the in each case disc-closed volume regions 12 or 12 ', a higher degree of filling of conveyed goods is achieved there.
Die Erfindung ermöglicht es, dass die Förderstrecke 14 verkürzbar ist und auf zwei "Hohlraumlängen" bzw. auf eine "Eint agshohlraum-Hohlraum-Austragshohlraum"-Anordnung 15-16- 17 bezogen werden kann. Wahlweise kann die Förderstrecke 14 auf einen Schneckengang des Stators 2 verkürzt sein.The invention enables the conveyor path 14 to be shortened and to be able to relate to two “cavity lengths” or to a “single-cavity-cavity-discharge-cavity” arrangement 15-16-17. Optionally, the conveyor section 14 can be shortened to a worm gear of the stator 2.
Durch die Anbringung des erfindungsgemäßen Rotorkopfteils, insbesondere der Rotorlochscheibe 7 am bisherigen Rotorendteil von Exzenterschneckenpumpen und der mit den Vorteilen verbundenen möglichen Verkürzung auch von bereits produzierten Ex- zenterschneekenpumpen mit relativ langen Statoren und Rotoren kann die erforderliche Antriebsleistung mittels eines auch leistungsverringerten Motors erreicht werden, wobei somit auch Energie und Material eingespart werden können.By attaching the rotor head part according to the invention, in particular the perforated rotor disk 7 to the previous rotor end part of eccentric screw pumps and the possible shortening associated with the advantages, even of eccentric screw pumps already produced with relatively long stators and rotors, the required drive power can be achieved by means of a motor which is also reduced in power, whereby thus energy and material can also be saved.
Eine Erhöhung des Förderdruckes wird grundsätzlich durch eine Erhöhung der Vorspannung zwischen dem Stator 2 und dem Rotor 3 erreicht, was in herkömmlicher Weise in der Regel achsialflächig z.B. mittels eines den Stator 2 umfassenden Spannmantels erfolgt. Ein Problem besteht darin, dass damit ein entsprechend erhöhter Energieaufwand zum Pumpenbetrieb verbunden ist.An increase in the delivery pressure is fundamentally achieved by an increase in the pretension between the stator 2 and the rotor 3, which in a conventional manner usually has an axial surface e.g. by means of a clamping jacket comprising the stator 2. One problem is that this involves a correspondingly increased energy expenditure for pump operation.
Um die erfindungsgemäße Exzenterschneckenpumpe 1 auch unter erhöhten Förderdrücken energetisch effizient zu betreiben, ist eine entsprechende Vorspannungserhöhung in radialer Richtung zur Pumpenmittelachse 26 gerichtet mit geringstmöglicher ach- sialer Ausformung vorgesehen. Dabei kann in den Bereichen des Stators 2 in vorzugsweise ganzzahligen Abständen eines einer Umdrehung entsprechenden Schneckenmantelgewindeganges von der Rotorstirnfläche 6 aus entfernt wahlweise eine radiale Querschnittsverjüngung vorgesehen sein.In order to operate the eccentric screw pump 1 according to the invention in an energy-efficient manner even under elevated delivery pressures, a corresponding increase in preload in the radial direction to the pump center axis 26 is provided with the least possible axial shape. A radial cross-sectional taper can optionally be provided in the regions of the stator 2, preferably in integer intervals of a screw casing thread corresponding to one revolution, from the rotor end face 6.
Bei einem mehr als einen Schneckenmantelgewindegang aufweisenden Stator 2 kann in etwa einem einem Schneckenmantelgewinde- gang des Stators 2 entsprechenden Abstand von der Rotorstirnfläche 6 aus entfernten Bereich dem Stator 2 ein radiales Querschnittsverjüngungselement (nicht eingezeichnet) zugeordnet sein.In the case of a stator 2 having more than one worm shell thread, a radial cross-sectional tapering element (not shown) can be assigned to the stator 2 at a distance from the rotor end face 6 corresponding to a worm shell thread of the stator 2.
Das radiale Querschnittsverjüngungselement kann als ein Elementesystem innerhalb und/oder außerhalb des Statormantels 29 manschettenartig ausgebildet und angeordnet sein, das wahlweise steuerbar oder über Stellglieder regelbar in radialer Richtung veränderbar und mit dem die radiale Vorspannung der Ab- dichtungsbereiche 23,24 des Stators 2 gegenüber dem Rotor 3 entweder schrittweise oder kontinuierlich in Abhängigkeit vom vorgegebenen Förderdruck einstellbar ist.The radial cross-sectional tapering element can be configured and arranged in the manner of a sleeve inside and / or outside of the stator casing 29, which can be changed in the radial direction, either in a controllable manner or via actuators, and with which the radial prestressing of the sealing areas 23, 24 of the stator 2 with respect to that Rotor 3 can be adjusted either step by step or continuously depending on the specified delivery pressure.
Die Erfindung eröffnet die Möglichkeit, dass neben der zeitli- chen Verzögerung der Verschleißausbildung auch die Herstellungskosten gegenüber den komplizierten Ausbildungen von bekannten nachspannbaren und nicht nachspannbaren Exzenterschneckenpumpen sowie bekannten Rückschlagventileinrichtungen am Statorendbereich von Exzenterschneckenpumpen verringert werden können. BezugsseichenlisfceThe invention opens up the possibility that, in addition to the time delay in the formation of wear, the manufacturing costs can also be reduced compared to the complicated designs of known re-tensionable and non-re-tensionable eccentric screw pumps and known check valve devices at the stator end area of eccentric screw pumps. Bezugsseichenlisfce
1 Exzenterschneckenpumpe1 eccentric screw pump
2 Stator2 stator
3 Rotor 4 saugseitiger Eingangsbereich3 Rotor 4 input area on the suction side
5 druckseitiger Austragsbereich5 discharge area on the pressure side
6 Rotorstirnfläche6 rotor face
7 erstes Rotorkopfteil7 first rotor head part
8 durchgängige Ausnehmung 9 Rotorkopfteilfrontfläche8 continuous recess 9 rotor head part front surface
10 Rotationsförderrichtung10 direction of rotation
11 erster Druck-Volumenbereich 11' zweiter Druck-Volumenbereich11 first pressure volume range 11 'second pressure volume range
12 erster Saug-Volumenbereich 12 ' zweiter Saug-Volumenbereich12 first suction volume area 12 'second suction volume area
13 lochfreier Rotorkopfteilbereich13 hole-free rotor head section
14 Förderstrecke14 conveyor line
15 saugseitiger Eintragshohlraum15 suction-side entry cavity
16 mittlerer Förderhohlraum 17 druckseitiger Austragshohlraum16 middle conveying cavity 17 discharge-side discharge cavity
18 Statorinnenfläche18 stator inner surface
19 Rotoraußenfläche19 rotor outer surface
20 erste Förderkammer20 first delivery chamber
21 zweite Förderkammer 22 dritte Förderkammer21 second delivery chamber 22 third delivery chamber
23 erster Abdichtungsbereich23 first sealing area
24 zweiter Abdichtungsbereich24 second sealing area
25 Statorstirnfläche25 stator face
26 Pumpenmittelachse 27 Statoröffnung26 pump central axis 27 stator opening
28 Rotorstirnflächenmittelpunkt bei α = 0°, ' Rotorstirnflächenmittelpunkt bei α = 90°, '' Rotorstirnflächenmittelpunkt bei α - 180°, Statormantel Rotorkopfteilrückfläche Sektorartige Aussparung Sektorabschnittsförmige Durchgangsöffnung Rotorkopfteilmittelachse Druckrohr Lochanfangsbereich Lochendebereich zweites Rotorkopfteil 28 rotor end face center point at α = 0 °, '' Rotor end face center point at α = 90 °, '' Rotor end face center point at α - 180 °, stator jacket rotor head part rear surface Sector-like recess Sector section-shaped through opening rotor head part center axis pressure pipe hole start area hole end area second rotor head part

Claims

afcf≥ϊϊ ξiΩs üclϊe afcf≥ϊϊ ξiΩs üclϊe
1. Exzenterschneckenpumpe (1), die einen Stator (2) und einen Rotor (3) aufweist, zwischen denen das Fördergut beim Drehen des Rotors (3) im Stator (2) von einem saugseitigen Eingangsbereich (4) zu einem druckseitigen Austragsbereich (5) verschoben wird, wobei sich im druckseitigen Austragsbereich (5) ein Druck-Volumenbereich (11) und ein Saug- Volumenbereich (12) zwischen dem Stator (2) und dem Rotor (3) rotordrehungsbedingt sich ändernd und wechselnd gegenüberliegen, dadurch gekennzeichnet, dass ein den druckseitigen Austragsbereich (5) abschlie- ßendes, an der Stirnfläche (6) des Rotors (3) befestigtes, sich mit dem Rotor (3) drehendes Rotorkopfteil (7) vorgesehen ist, das mindestens eine kopfteildurchgängige Ausnehmung (8) aufweist, die in Bezug zur halternden Rotorstirnfläche (6) derart in das Rotorkopfteil (7) einge- bracht ist, dass die sich mit dem Rotor (3) in Förderrichtung (10) konform drehende Ausnehmung (8) den Druck- Volumenbereich (11,11') begleitend öffnet und dass ein ausneh ungsfreier Rotorkopfteilbereich (13) während der Öffnungsdauer des Druck-Volumenbereiches (11,11') den ge- genüberliegenden Saug-Volumenbereich (12,12') abdichtend verschlossen hält. 1. eccentric screw pump (1), which has a stator (2) and a rotor (3), between which the material to be conveyed when the rotor (3) rotates in the stator (2) from an intake-side input area (4) to a pressure-side discharge area (5 ) is displaced, with a pressure-volume area (11) and a suction-volume area (12) between the stator (2) and the rotor (3) being opposite and changing due to the rotation of the rotor, in the discharge-side discharge area (5), characterized in that A discharge head region (5), which closes off the discharge side (5) and is attached to the end face (6) of the rotor (3) and rotates with the rotor (3), is provided which has at least one recess (8) which is continuous with the head part in relation to the holding rotor end face (6) is introduced into the rotor head part (7) in such a way that the recess (8) which rotates in the conveying direction (10) in conformity with the rotor (3) covers the pressure / volume range (11, 11 ') accompanying opens and that an extension-free rotor head part area (13) keeps the opposite suction volume area (12, 12 ') sealed during the opening period of the pressure volume area (11, 11').
2. Exzenterschneckenpumpe nach Anspruch 1, dadurch gekennzeichnet, dass das Rotorkopfteil (7) eine derartige Umfangs- Dimensionierung aufweist, dass das Rotorkopfteil (7) bei Drehung den Druck-Volumenbereich (11,11') öffnet und den Saug-Volumenbereich (12,12') im Bereich der Statoröffnung (27) verschlossen hält.2. Eccentric screw pump according to claim 1, characterized in that the rotor head part (7) has such a circumferential dimensioning that the rotor head part (7) opens the pressure volume area (11, 11 ') and the suction volume area (12, 12 ') in the area of the stator opening (27).
3. Exzenterschneckenpumpe nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, dass die Befestigung des Rotorkopfteils (7) an der Rotorstirnfläche (6) durch Verschraubung, Verschweißung od.dgl. mit der Rotorkopfteilrückfläche (30) herbeige- führt ist, wobei die restliche Rotorkopfteilrückfläche (30) und die Statorstirnfläche (25) ebenflächig sind und mit der Pumpenmittelachse (26) einen Winkel von ca. 90° bilden.3. eccentric screw pump according to claim 1 and / or 2, characterized in that the attachment of the rotor head part (7) on the rotor end face (6) by screwing, welding or the like. is brought about with the rotor head part rear surface (30), the remaining rotor head part rear surface (30) and the stator end face (25) being flat and forming an angle of approximately 90 ° with the pump center axis (26).
4. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die durchgängige Ausnehmung (8) vorzugsweise unmittelbar seitlich an der Stirnfläche (6) des Rotors (3) in das Rotorkopfteil (7) eingebracht ist, wobei der Ausnehmungsquerschnitt dimensionierungskonform mit dem Austrag von Fördergut aus dem Druck-Volumenbereich (11,11') durch den sich drehenden Rotor (3) vorgegeben ist.4. Eccentric screw pump according to at least one of the preceding claims, characterized in that the continuous recess (8) is preferably made directly to the side on the end face (6) of the rotor (3) in the rotor head part (7), the recess cross section conforming to the dimensions of the discharge of conveyed material from the pressure volume range (11, 11 ') is predetermined by the rotating rotor (3).
5. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die durchgängige Ausnehmung (8) des Rotorkopfteils (7) wahlweise als eine vorzugsweise vom Rand der haltern- den Rotorstirnfläche (6) ausgehende, radial gerichtete sektorabschnittsförmige Durchgangsöffnung (32) oder sek- torartige Aussparung (31) ausgebildet ist, die jeweils mit ihrem wirksamen Öffnungsquerschnitt rotorkonform mit der Druckerzeugung innerhalb des Druck-Volumenbereic es (11, 11') in den Druck-Volumenbereich (11,11') eintritt und nach Überstreichung des Druck-Volumenbereiches (11,11') wieder aus dem Druck-Volumbereich (11,11') heraustritt.5. Eccentric screw pump according to at least one of the preceding claims, characterized in that the continuous recess (8) of the rotor head part (7) is optionally designed as a radially directed sector-section-shaped through opening (32) or sector-like recess (31), preferably starting from the edge of the holding rotor end face (6), each with its effective opening cross-section rotor-conform with the pressure generation within the pressure volume range (11, 11 ') enters the pressure volume range (11, 11') and after the pressure volume range (11, 11 ') has been exceeded, again from the pressure volume range ( 11, 11 ') emerges.
6. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Rotorkopfteil (7) vorzugsweise eine Rotorlochscheibe ist und die durchgängige Ausnehmung (8) vorzugsweise ein im draufsichtigen Querschnitt weitgehend boh- nenförmiges Langloch darstellt.6. Eccentric screw pump according to at least one of the preceding claims, characterized in that the rotor head part (7) is preferably a rotor perforated disc and the continuous recess (8) preferably represents a largely bean-shaped elongated hole in plan cross section.
7. Exzenterschneckenpumpe nach Anspruch 6, dadurch gekennzeichnet, dass die Rotorlochscheibe (7) an der Rotorstirnfläche (6) derart befestigt ist, dass die Mittelachse (33) der Ro- torlochscheibe (7) wahlweise mit dem Mittelpunkt (28) der Rotorstirnfläche (6) übereinstimmt.7. Eccentric screw pump according to claim 6, characterized in that the rotor perforated disk (7) is attached to the rotor end face (6) such that the central axis (33) of the rotor perforated disk (7) optionally with the center (28) of the rotor end face (6 ) matches.
8. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Rotorlochscheibe (7) derart an der Rotorstirnfläche (6) angebracht ist, dass das Loch (8) mit seinem wirksamen Öffnungsquerschnitt rotorkonform mit der Druckerzeugung innerhalb des Druck-Volumenbereiches (11,11') mit dem Lochanfangsbereich (35) in den Druck- Volumenbereich (11,11') eintritt und nach Überstreichung des Druck-Volumenbereiches (11,11') mit dem Lochendebereich (36) aus dem Druck-Volumbereich (11,11') heraustritt.8. Eccentric screw pump according to at least one of the preceding claims, characterized in that the rotor perforated disc (7) is attached to the rotor end face (6) such that the hole (8) with its Effective opening cross section conforming to the rotor with the pressure generation within the pressure volume range (11, 11 ') with the hole beginning area (35) enters the pressure volume range (11, 11') and after sweeping over the pressure volume range (11, 11 ') with the Hole end area (36) emerges from the pressure volume area (11, 11 ').
9. Exzenterschneckenpumpe nach mindestens einem der vorher- gehenden Ansprüche, dadurch gekennzeichnet, dass die Rotorkopfteilrückfläche (30) und die Statorstirnfläche (25) ebenflächig ausgebildet sind und jeweils einen Winkel von ca. 90° zur Pumpenmittelachse (26) auf- weisen.9. Eccentric screw pump according to at least one of the preceding claims, characterized in that the rotor head part rear surface (30) and the stator end face (25) are flat and each have an angle of approximately 90 ° to the pump center axis (26).
10. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die der Rotorstirnfläche (6) abgewandte Rotorkopf- teilfrontflache (9) wahlweise ebenflächig bezüglich der scheibenförmigen Ausbildung, kugelkalottenförmig und/oder mit mindestens einem Flügel oder anderen Vorsprüngen aufweisendem Profil zur Durchsatz- und Mischverbesserung des Fördergutes versehen ist.10. Eccentric screw pump according to at least one of the preceding claims, characterized in that the rotor end face (6) facing away from the rotor head part front surface (9) optionally flat with respect to the disk-shaped design, spherical cap-shaped and / or with at least one wing or other projections having a profile for throughput. and mixing improvement of the conveyed material is provided.
11. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Rotor (3) als Schnecke in Form einer Rundgewindeschraube mit hoher Steigung und großer Gewindetiefe ausgebildet ist, wobei der Stator (2) einen Schneckenman- tel darstellt und axial nacheinander ausgebildete Hohlräume (15,16,17) - zumindest einen saugseitigen Eintragshohlraum (15) und einen druckseitigen Austragshohlraum (17) - einer Förderstrecke (14) enthält, wobei sich zwi- sehen der Statorinnenfläche (18) und der Rotoraußenfläche (19) Förderkammern (20,21,22) durch zwischen dem Stator (2) und dem Rotor (3) angepasste Abdichtungsbereiche (23,24) ausbilden, wobei das Fördergut in den Förderkammern (20,21,22) beim Drehen des Rotors (3) in den Hohl- räumen (15,16,17) des Stators (2) vom saugseitigen Eingangsbereich (4) zum druckseitigen Austragsbereich (5) verschiebbar ist.11. Eccentric screw pump according to at least one of the preceding claims, characterized in that the rotor (3) is designed as a screw in the form of a round screw with a high pitch and a large thread depth, the stator (2) having a screw represents tel and axially successively formed cavities (15,16,17) - at least one suction-side entry cavity (15) and a discharge-side discharge cavity (17) - a conveyor section (14), between the stator inner surface (18) and the rotor outer surface (19) Form conveying chambers (20, 21, 22) by sealing areas (23, 24) adapted between the stator (2) and the rotor (3), the material to be conveyed in the conveying chambers (20, 21, 22) when the rotor is rotated (3) in the cavities (15, 16, 17) of the stator (2) can be moved from the suction-side inlet area (4) to the discharge-side discharge area (5).
12. Exzenterschneckenpumpe nach mindestens einem der vorher- gehenden Ansprüche, dadurch gekennzeichnet, dass auf der Statorstirnfläche (25) ein Druckrohr (26) befestigbar ist, über das das Fördergut weitergeleitet wird, wobei das Druckrohr (26) mittels mindestens eines vorzugsweise stator- und druckrohru fassenden Halterungselementes abgedichtet am Stator (2) arretierbar ist.12. Eccentric screw pump according to at least one of the preceding claims, characterized in that on the stator end face (25) a pressure tube (26) can be fastened, via which the material to be conveyed is passed, the pressure tube (26) by means of at least one preferably stator and pressure pipe mounting bracket sealed on the stator (2) can be locked.
13. Exzenterschneckenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass wahlweise eine Anpressvorrichtung im Bereich des Druckrohres (26) für das Rotorkopfteil (7) an die Stirnfläche (25) des Stators (2) zur verstärkten Abdichtung des Saug-Volumenbereiches (12,12') zwischen Rotor (3) und Stator (2) vorgesehen ist. 13. Eccentric screw pump according to at least one of the preceding claims, characterized in that optionally a pressing device in the region of the pressure tube (26) for the rotor head part (7) on the end face (25) of the stator (2) for the reinforced sealing of the suction volume region (12 , 12 ') between the rotor (3) and stator (2) is provided.
14. Exzentersehneekenpumpe nach mindestens einem der vorher gehenden Ansprüche, dadurch gekennzeichnet, dass die Förderstrecke (14) vorzugsweise auf zwei Hohl- raumlängen bzw. auf eine "Eintragshohlraum-Hohlraum- Austragshohlraum" -Anordnung (15-16-17) bezogen ist.14. Eccentric tendon pump according to at least one of the preceding claims, characterized in that the conveying path (14) is preferably based on two cavity lengths or on an "entry cavity-discharge-cavity" arrangement (15-16-17).
15. Exzentersehneekenpumpe nach mindestens einem der vorher gehenden Ansprüche, dadurch gekennzeichnet, dass die Förderstrecke (14) auf einen Schneckengang des Stators (2) verkürzt ist, wobei das Rotorkopfteil (7) insbesondere zur Lagestabilisierung des Rotors (3) beiträgt .15. Eccentric tendon pump according to at least one of the preceding claims, characterized in that the conveying path (14) is shortened to a worm gear of the stator (2), the rotor head part (7) contributing in particular to stabilizing the position of the rotor (3).
16. Exzentersehneekenpumpe nach mindestens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass in den Bereichen des Stators (2) in vorzugsweise ganzzahligen Abständen eines einer Umdrehung entsprechenden Schneckenmantelgewindeganges von der Rotorstirnfläche (6) aus entfernt wahlweise eine radiale Querschnittsverjüngung vorgesehen ist.16. Eccentric tendon pump according to at least one of the preceding claims, characterized in that a radial cross-sectional taper is optionally provided in the areas of the stator (2), preferably in integer intervals of a screw casing thread turn corresponding to one revolution, from the rotor end face (6).
17. Exzentersehneekenpumpe nach Anspruch 16, dadurch gekennzeichnet, dass bei einem mehr als einen Schneckenmantelgewindegang aufweisenden Stator (2) in etwa einem einem Schneckenmantelgewindegang des Stators (2) entsprechenden Abstand von der Rotorstirnfläche (6) aus entfernten Bereich dem Stator (2) ein radiales Querschnittsverjüngungselement zugeordnet ist .17. Eccentric tendon pump according to claim 16, characterized in that in the case of a stator (2) having more than one worm shell thread pitch, a distance from the rotor end face (6) corresponding to a worm shell thread pitch of the stator (2) is removed a radial cross-sectional tapering element is assigned to the stator (2).
18. Exzentersehneekenpumpe nach Anspruch 17, dadurch gekennzeichnet, dass das radiale Querschnittsverjüngungselement als ein Elementesystem innerhalb und/oder außerhalb des Statormantels (29) manschettenartig ausgebildet und angeordnet ist, das wahlweise steuerbar oder über Stellglieder regelbar in radialer Richtung veränderbar ist und mit dem die radiale Vorspannung der Abdichtungsbereiche (23,24) des Stators (2) gegenüber dem Rotor (3) entweder schrittweise oder kontinuierlich in Abhängigkeit vom vorgegebenen Förderdruck einstellbar ist. 18. Eccentric tendon pump according to claim 17, characterized in that the radial cross-sectional tapering element is designed and arranged in a sleeve-like manner as an element system inside and / or outside of the stator casing (29), which is optionally controllable or adjustable via actuators in the radial direction and with which the radial one Biasing of the sealing areas (23, 24) of the stator (2) relative to the rotor (3) can be adjusted either step by step or continuously depending on the specified delivery pressure.
EP04719362A 2003-03-12 2004-03-11 Eccentric screw pump Expired - Lifetime EP1601875B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE20304292U 2003-03-12
DE20304292U DE20304292U1 (en) 2003-03-12 2003-03-12 Cavity Pump
PCT/DE2004/000538 WO2004081385A1 (en) 2003-03-12 2004-03-11 Eccentric screw pump

Publications (2)

Publication Number Publication Date
EP1601875A1 true EP1601875A1 (en) 2005-12-07
EP1601875B1 EP1601875B1 (en) 2006-07-05

Family

ID=7980896

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04719362A Expired - Lifetime EP1601875B1 (en) 2003-03-12 2004-03-11 Eccentric screw pump

Country Status (6)

Country Link
EP (1) EP1601875B1 (en)
CN (1) CN100429402C (en)
AT (1) ATE332443T1 (en)
DE (3) DE20304292U1 (en)
ES (1) ES2268641T3 (en)
WO (1) WO2004081385A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013003833A1 (en) 2013-03-07 2014-09-11 Wilo Se Pump with overpressure protection
CN104405631B (en) * 2014-09-30 2016-06-01 余雷 A kind of can the pump head of deep water intake
CN106685152B (en) * 2015-11-10 2019-03-12 耐驰（兰州）泵业有限公司 Manufacture for eccentrie helical totorpump can hydraulic adjustment stator method
CN108000836B (en) * 2017-12-11 2023-08-29 华南理工大学 Melt conveying flow balance compensation method and stabilizing device of eccentric rotor extruder

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
HU175810B (en) * 1977-12-28 1980-10-28 Orszagos Koolaj Gazipari Axial-flow multiple-purpose flow apparatus
DE3641855A1 (en) * 1986-12-08 1988-06-16 Allweiler Ag Werk Bottrop Adjustable stator for eccentric screw pumps
US4802827A (en) * 1986-12-24 1989-02-07 Kabushiki Kaisha Toshiba Compressor
JP2897844B2 (en) * 1990-10-26 1999-05-31 兵神装備株式会社 Single shaft eccentric screw pump
CN2100511U (en) * 1991-04-16 1992-04-01 王时正 Internal engagement epicycloidal oil pump
DE20215849U1 (en) * 2002-10-10 2003-01-09 Löffler, Norbert, Dr., 01734 Rabenau Helical pump has stator and rotor discharging via back-flow prevention valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004081385A1 *

Also Published As

Publication number Publication date
EP1601875B1 (en) 2006-07-05
ES2268641T3 (en) 2007-03-16
WO2004081385A1 (en) 2004-09-23
DE502004000924D1 (en) 2006-08-17
DE20304292U1 (en) 2003-05-15
ATE332443T1 (en) 2006-07-15
CN100429402C (en) 2008-10-29
CN1791750A (en) 2006-06-21
DE112004000856D2 (en) 2006-02-02
WO2004081385A8 (en) 2006-02-16

Similar Documents

Publication Publication Date Title
EP1012448B1 (en) Oil pump module with filter, in particular for internal combustion engine lubricating oil
EP2818721B1 (en) Centrifugal pump
EP0536159A1 (en) Assembly for feeding fuel from the fuel tank of a motor vehicle to its internal combustion engine.
EP2910783B1 (en) Dual spindle helical spindle pump with a single-entry design
DE102009047643A1 (en) Internal gear pump e.g. hydraulic pump, for conveying brake fluid in hydraulic vehicle brake system, has filling piece including spring whose legs are processed in circumferential direction and act inwardly and outwardly opposite to heads
DE7625941U1 (en) ROTOR DISPENSER MACHINE WITH A SCREW
EP0796154B1 (en) High-pressure cleaning device
DE102013003833A1 (en) Pump with overpressure protection
WO2012103923A1 (en) Internal gear pumps for a hydraulic vehicle braking system
WO2002018798A1 (en) Aggregate for conveying fuel
EP1880108A1 (en) Internal gear fuel pump
DE10024741B4 (en) Side channel pump
EP1601875A1 (en) Eccentric screw pump
DE3434694A1 (en) SCREW COMPRESSOR FOR GASEOUS MEDIA
EP1832750B1 (en) Outer gear pump with a pressure relief recess
WO2021009275A1 (en) Stator for an eccentric screw pump
EP0642913B1 (en) Single screw extruder with gear pump
DE4437377B4 (en) Aggregate for conveying fuel from a storage tank to an internal combustion engine
DE1284156B (en) Gear pump for supplying internal combustion engines with fuel
EP1310672B1 (en) Fuel pump for a fuel system of an internal combustion engine and fuel system
DE3045192C2 (en) Gear pump
EP1276992A1 (en) Gear-wheel pump, in particular for a high-pressure fuel pump
EP0661454A1 (en) Internal gear pump
DE4426761C2 (en) screw compressors
EP2342464A1 (en) Side channel blower, in particular secondary air blower for an internal combustion engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051005

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ROESNER, PETER

Owner name: STEGNER, ANKE

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

DAX Request for extension of the european patent (deleted)
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060705

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502004000924

Country of ref document: DE

Date of ref document: 20060817

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061005

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061005

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061005

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20061003

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061205

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2268641

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070410

BERE Be: lapsed

Owner name: ROSNER, PETER

Effective date: 20070331

Owner name: STEGNER, ANKE

Effective date: 20070331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061006

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070311

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20080601

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070311

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060705

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070106

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20100325

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20100423

Year of fee payment: 7

Ref country code: FR

Payment date: 20100415

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100311

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20100323

Year of fee payment: 7

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20110616

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110311

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20111130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110311

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20110616

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20120424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110312

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20120405

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004000924

Country of ref document: DE

Effective date: 20131001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131001